Spring holding connectors

ABSTRACT

A spring holding connector includes a housing having a bore therethrough and a shaft rotatably and slidably received in the bore, a circular groove is in one of said bore and shaft and a circular spring disposed in the groove for slidably holding said shaft within the bore. The groove is sized and shaped for controlling, in combination with a spring configuration, shaft mobility within the bore.

[0001] The present invention relates to canted coil springs that aremounted in grooves that can either be disposed in a housing or the shaftfor the purpose of holding such shaft or housing from movement which canbe axial or rotary and in some cases, permit the passing of current fromthe housing through the spring onto the shaft and vice versa. Retaininga shaft or a housing offers some significant advantages in case where acertain force needs to be developed to hold a piston or shaft and at thesame time provide other benefits, such as electrical conductivity,shielding against EMI and others.

[0002] Connectors used in holding applications have been describedextensively, as for example, U.S. Pat. Nos. 4,974,821, 5,139,276,5,082,390, 5,545,842, 5,411,348 to Balsells, and others. All of thesepatents are to be incorporated herewith by this specific referencesthereto.

[0003] Of these cited U.S. Pat. No. 4,974,821 generally describes cantedcoil springs and a groove for orienting the spring for major axis radialloading for enabling a specific preselected characteristic in responseto loading of the spring.

[0004] U.S. Pat. No. 5,082,390 teaches a canted coil spring for holdingand locking a first and second number to one another.

[0005] U.S. Pat. No. 5,139,276 discloses a radially loaded spring in agroove for controlling resilient characteristics of the spring.

[0006] U.S. Pat. No. 5,411,348 and 5,545,842 teach spring mechanismswhich preferentially lock two members together.

[0007] None of the cited references or any prior art provides forcontrolling shaft mobility within a bore.

[0008] This patent invention provides for various types of novel groovedesigns disposed in a piston, a shaft, and/or housing. Different springdesign configurations are provided that affect holding, force variation,resistivity variation, and other variations under static and dynamicloading conditions between the housing, the spring, and the shaft byappropriate groove, spring and material combinations.

SUMMARY OF THE INVENTION

[0009] A spring holding connector in accordance with the presentinvention generally includes a housing having a bore therethrough withshaft rotatably and/or slidably received within the bore.

[0010] A circular groove is formed in either the bore or the shaft and acircular spring is disposed in the groove for slidably holding the shaftwithin the bore. Importantly, the groove is sized and shaped, incombination with a spring configuration, for controlling shaft mobilitywithin the bore.

[0011] This causes movement of the shaft within the bore to requirediffering forces dependent upon direction of shaft movement.

[0012] In one embodiment of the present invention, a spring is turnablewithin the groove for causing forces required to move the shaft withinthe bore and be dependent upon the direction of the movement. In anotherembodiment, the spring is compressible within the groove for causingforces required to move the shaft within the bore to be dependent upon adirection of movement. Both turning and compression of the spring incombination further, in combination, provide for a differentiation offorces necessary to move the shaft within the bore to be dependent uponthe direction of movement.

[0013] Such movement may be axial and further the spring may be turnablein the groove for enabling electroconductivity between the shaft and thehousing to be improved by removing oxidation which may form on thespring. In this embodiment, the groove may include an uneven bottom forscraping the spring as the spring turns therepast.

[0014] In accordance with the present invention, the spring may be acounterclockwise radial spring or a clockwise radial spring dependingupon the shaft mobility requirements.

[0015] Alternatively, the spring may be an axial spring having a backangle at an inside diameter of the spring coils and a front angle on anoutside diameter the spring coils.

[0016] Alternatively, the spring may be an axial spring having a backangle on an outside diameter of the springs, coils and a front angle onan inside diameter of the spring coils. This again is important inproviding the differential force requires as hereinabove noted.

[0017] More specifically, the groove may be sized and shaped for causinga combination of the spring combination a force required to move theshaft in one axial direction to be greater than about 300% of the forcerequired to move the shaft in an opposite axial direction. This forcedifferentiation may be as high as 1200% or more depending upon a grooveand a spring selection as hereinafter set forth.

[0018] In one embodiment of the present invention, the groove has atapered bottom and in another embodiment the groove may have a flatbottom.

[0019] The groove further may include a V-bottom, a tapered V-bottom, asemi-tapered V-bottom, or a round bottom with a shoulder thereon.

[0020] In addition, the connector may include the grooves with invertedV-bottoms with a different angles as subtending sides of the groove. Adovetail groove may also be utilized and the groove may include aninwardly facing lip disposed opposite a groove bottom all of the groove,all such embodiments being hereinafter described in greater detail.

BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The advantages and features of the present invention will bebetter understood by the following description when considered inconjunction with the accompanying drawings in which:

[0022]FIGS. 1a-1 e show different positions of a counter clockwiseradial spring;

[0023]FIGS. 2a-2 c show a counter clockwise radial spring and a flatbottom housing groove;

[0024]FIGS. 3a-3 c show a clockwise radial spring and a flat bottomhousing groove;

[0025]FIGS. 4a-4 b shows a RF clockwise axial spring and a taperedbottom groove;

[0026]FIGS. 5a-5 d shows an RF clockwise axial spring mounted in atapered bottom groove;

[0027]FIGS. 6a-6 c are similar to FIGS. 4a-4 d and 5 a-5 d with thespring mounted in a piston groove;

[0028]FIGS. 7a-7 c are similar to FIGS. 6a-6 c shown a differentdirection of shaft movement;

[0029]FIGS. 8a-8 c and 9 a-9 c make a comparison to the configurationshown in FIGS. 4 and 5 in which an F axial spring is utilized;

[0030]FIGS. 10a-10 c and 11 a-11 c shown an F spring mount in a piston;

[0031]FIGS. 12a-12 g show a counter clockwise radial spring turn 90°clockwise into a counter clockwise axial F spring and assembled in agroove with the groove width smaller than the coil height;

[0032]FIGS. 13a-13 g show a counter clockwise radial spring turn 90°clockwise into a clockwise axial RF spring assembled in a groove withthe groove width smaller than the coil height;

[0033]FIGS. 14a-14 g show a counter clockwise radial spring turn 90°clockwise into a clockwise axial RF spring and assembled in a groovewith a groove width smaller than the coil height;

[0034]FIGS. 15a-15 g show a counter clockwise radial spring turn 90°clockwise into a counter clockwise axial F spring and assembled in agroove with a groove width smaller than the coil height;

[0035]FIGS. 16a-16 b and 17 a-17 b show axial RF and F springs with ashaft shown moving in a concave direction of the spring ID as shown inFIGS. 16a and 16 b and FIGS. 17a-17 b showing the shaft moving in aconvex direction of the spring ID;

[0036]FIGS. 18 and 19 illustrates that when a pin is moved away from aturn angle “A” the running force developed a substantially less thanwhen the pin moves toward the tapered angle “A”, with the spring turningclockwise;

[0037]FIGS. 20a-20 c show radial spring in which the free spring outsidediameter is greater than the bore outside diameter;

[0038]FIG. 21a-21 c shows a radial spring in which the free springoutside diameter is equal to the bore outside diameter;

[0039]FIGS. 22a-22 c show radial spring mounted in a piston in which thespring ID is smaller than the piston groove diameter;

[0040]FIGS. 23a-23 c show a radial spring mounted on a piston in whichthe spring ID is equal to a piston groove diameter;

[0041]FIG. 24 shows the radial spring compression with various housingbore diameters;

[0042]FIG. 25 illustrates a constant housing bore diameter with avariable shaft diameter;

[0043]FIGS. 26a-26 b illustrate F springs versus RF springs mounted in ahousing;

[0044]FIGS. 27a-27 b show F springs versus RF springs mounted on apiston;

[0045]FIGS. 28a-28 c show a variation of an RF spring diameter and itseffect on forces;

[0046]FIGS. 29a-29 c compare the variation of an F spring diameter andits effect on force; and

[0047]FIGS. 30-37 show different kinds of groove spring configurationshaving a flat bottom groove, both on the housing and on the piston usingaxial springs and a groove in which the groove width is smaller than thegroove height.

DETAILED DESCRIPTION

[0048] An overview or general description of spring and grooveconfigurations as well as various definitions to enable andunderstanding of the present invention is appropriate. In the presentapplication, the groove configurations have been divided into two types:one type with the spring retained in the housing as shown in Tables1a-1j and the other with the spring retained in a shaft, as shown inTables 2a-2h which also provides design features and characteristics ofthe holding connectors in accordance with the present invention.

[0049] The springs are divided in two types: a radial spring and anaxial spring.

[0050] Definition of radial canted coil spring. A radial canted coilspring has its compression force perpendicular or radial to thecenterline of the arc or ring.

[0051] Definition of axial canted coil spring. An axial canted coilspring has its compression force parallel or axial to the centerline ofthe arc or ring.

[0052] The spring can also assume various angular geometries, varyingfrom 0 to 90 degrees and can assume a concave or a convex position inrelation to the centerline of the spring.

[0053] Definition of concave and convex. For the purpose of this patentapplication, concave and convex are defined as follows: The positionthat a canted coil spring assumes when a radial or axial spring isassembled into a housing that has a groove width smaller than the coilheight and upon passing a pin through the ID of such spring, the springis positioned by the inserting pin so that the ID is forward of thecenterline of the minor axis of the spring cross section is a concaveposition.

[0054] When the spring is assembled in the piston, upon passing thepiston through a housing, the spring is positioned by the housing so theOD of the spring is behind the centerline of the minor axis of thespring cross section is a convex position.

[0055] The spring-rings can also be extended for insertion into thegroove or compressed into the groove. Extension of the spring consistsof making the spring ID larger by stretching or gartering the ID of suchspring to assume a new position when assembled into a groove or thespring can also be made larger than the groove cavity and compressedaround the outside diameter to assume a smaller outside diameter to fitthe groove inside diameter.

[0056] Canted coil springs are available in radial and axialapplications. Generally, a radial spring is assembled so that it isloaded radially. An axial spring is generally assembled into a cavity sothat the radial force is applied along the major axis of the coil, whilethe coils are compressed axially and deflect axially.

[0057] Radial springs. Radial springs can have the coils cantingcounterclockwise (Table 1a, row 2, column 6) or clockwise (Table 1a, row3, column 6). When the coils cant counterclockwise, the front angle isin front (FIG. 2c) with the back angle in the back and when the coilscant clockwise (FIG. 3a), the back angle is in the front and the frontangle is in the back. Upon inserting a pin or shaft through the insidediameter of the spring with such spring mounted in the housing in acounterclockwise position (FIG. 2c), the shaft will come in contact withthe front angle of the coil and the force developed during insertionwill be less than when compressing the back angle with the spring in aclockwise position. The degree of force will vary depending on variousfactors as hereinafter discussed. The running force will be about thesame.

[0058] Radial springs may also be assembled into a cavity whose groovewidth is smaller than the coil height. Assembly into such cavity can bedone by turning the spring coils clockwise or counterclockwise 90° andassembling the spring into the cavity. Under such conditions, the springwill assume an axial position, provided that the groove width is smallerthan the coil height. Under such conditions, the insertion and runningforce will be slightly higher than when an axial spring is assembledinto the same cavity. The reason is that upon turning the radial springat assembly, a torsional force is created, requiring a higher insertionand running force to pass a shaft through the inside diameter or othergroove configuration of the spring.

[0059] Axial springs. Axial springs can be RF (Table 1a, row 5, columns5 and 6) and F (Table 1a, row 6, columns 5 and 6). An RF spring (Table1a, row 5, column 6) is defined as one in which the spring ring has theback angle (FIG. 1e) at the ID of the coils with the front angle on theOD of the coils. An F spring (Table 1a, row 6, column 6) has the backangle at the OD and the front angle at the ID of the coils.

[0060] Turn angle ring springs. (Table 1h, row 4, column 6 to Table 1i,row 4, column 6) The springs can also be made with a turn angle and canassume a position from 0 to 90 degrees. It can have a concave (FIG. 4c)or a convex (FIG. 5c) position when assembled into the cavity, dependingon the direction in which the insertion pin is assembled that can affectthe insertion assembly and running force.

[0061] Assembly of axial spring ring into a cavity. F type axial springsalways develop a higher insertion and running force than an RF spring.The reason being is that in an F spring back angle is always located atthe OD of the spring, which develops a higher force.

[0062] Types of grooves that may be designed. Grooves may be classifiedin different designs.

[0063] Flat groove. (Table 1a, row 2, column 3 and row 3 column 3) Thesimplest type of groove is one that has a flat groove and the groovewidth is larger than the coil width of the spring. In such case, theforce is applied radially.

[0064] ‘V’ bottom groove. (Table 1a, row 4, column 3) This type ofgroove retains the spring better in the cavity by reducing axialmovement, increasing the points of contact, which enhances electricalconductivity and reduces the variability of such conductivity. Thegroove width is larger than the coil width. The spring force is appliedradially.

[0065] Grooves for axial springs. (Table 1a, row 5, column 2 to Table1b, row 5, column 2) Grooves for axial springs are designed to retainthe spring at assembly better. In such cases, the groove width issmaller than the coil height. At assembly, the spring is compressedalong the minor axis axially and upon the insertion of a pin or shaftthrough the ID of the spring the spring, the coils deflect along theminor axis axially.

[0066] There are variations of such type of grooves from a flat bottomgroove to a tapered bottom groove or modifications thereof.

[0067] Axial springs using flat bottom groove. In such cases, the degreeof deflection available on the spring is reduced compared to a radialspring, depending on the interference that occurs between the coilheight and the groove width.

[0068] The greater the interference between the spring coil height andthe groove, the lower the spring deflection and the higher the force todeflect the coils and the higher the insertion and running forces onshaft/pin insertion.

[0069] In such cases, the spring is loaded radially upon passing aplunger through the ID of such spring (Table 1a, row 5 to Table 1f, row3) and the deflection occurs by turning the spring angularly in thedirection of movement of the pin. An excessive amount of radialdeflection may cause permanent damage to the spring because the springcoils have “no place to go” and butt.

[0070] Axial springs with grooves with a tapered bottom. (Table 1c, row4, to Table 1d, row 5) A tapered bottom groove has the advantage thatpermits the spring to deflect gradually compared to a flat bottomgroove. When a pin is passed through the ID of the spring while suchspring is mounted in the groove, it will deflect in the direction ofmotion and the running force may remain about the same or vary dependingon the direction of the pin and the type of spring. Lower force willoccur when the pin moves in a concave spring position (FIG. 16b) andhigher force (FIG. 17b) that when the pin moves in a convex springposition.

[0071] Tapered bottom grooves have the advantages that they have asubstantial degree of deflection, which occurs by compressing the springalong the minor axis, thus allowing for a great degree of tolerancevariation as compared to flat bottom grooves.

[0072] Grooves can be mounted in the piston or in the housing, dependingon the application. Piston mounted grooves are shown in described Tables2a-2h.

[0073] Expanding a radial spring or compressing such spring. A radialspring ring can be expanded (FIGS. 21a, 21 b, and 21 c) from a smallinside diameter to a larger inside diameter and can also be compressedfrom a larger OD to a smaller OD (FIGS. 23a, 23 b, and 23 c) by crowdingthe OD of such spring into the same cavity. When expanding a springring, the back angle and front angles of the spring coils decrease (SeeFIGS. 1a to 1 e), thus increasing the connecting and running force. Whencompressing a radial spring OD into a cavity, which is smaller than theOD of such spring, the coils are deflected radially, causing the backand front angles to increase. The increase of such angles reduces theconnect and running force when passing a pin through the ID of suchspring.

[0074] The following designs are incorporated into the present patentapplication by this specific reference thereto as follows:

[0075] 1) U.S. Pat. No. 4,893,795 sheet 2 FIGS. 4, 5A, 5B, 5C, 5D, 5E,6A and 6B;

[0076] 2) U.S. Pat. No. 4,876,781 sheet 2 and sheet 3 FIGS. 5A, 5B, andFIG. 6.

[0077] 3) U.S. Pat. No. 4,974,821 page 3 FIGS. 8 and 9

[0078] 4) U.S. Pat. No. 5,108,078 sheet 1 FIGS. 1 through 6

[0079] 5) U.S. Pat. No. 5,139,243 page 1 and 2 FIGS. 1A, 1B, 2A, 2B andalso FIGS. 4A, 4B, 5A, and 5E

[0080] 6) U.S. Pat. No. 5,139,276 sheet 3 FIGS. 10A, 10B, 10C, 11A, 11B,12A, 12B, 12C, 13A, 13B, and 14

[0081] 7) U.S. Pat. No. 5,082,390 sheet 2 and 3, FIGS. 4A, 4B, 5A, 5B,6A, 6B, 7A, 7C, 8A, 8B

[0082] 8) U.S. Pat. No. 5,091,606 sheets 11, 12, and 14. FIGS. 42, 43,44, 45, 46, 47, 48, 48A, 48B, 49, 50A, 50B, 50C, 51A, 51B, 51C, 58A,58B, 58C, 58D.

[0083] 9) U.S. Pat. No. 5,545,842 sheets 1, 2, 3, and 5. FIGS. 1, 4, 6,9, 13, 14, 19, 26A, 26B, 27A, 27B, 28A, 28B.

[0084] 10) U.S. Pat. No. 5,411,348 sheets 2, 3, 4, 5, and 6. FIGS. 5A,5C, 6A, 6C, 7A, 7C, 7D, 8A, 8B, 8C, 9A, 9C, 10C, 11, 12 and 17.

[0085] 11) U.S. Pat. No. 5,615,870 Sheets 1-15, Sheets 17-23 with FIGS.1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20,21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33, 34, 35, 36, 37, 38,39, 40, 41, 42, 43, 44, 45, 46, 47, 48, 49, 50, 51, 52, 53, 54, 55, 56,57, 58, 59, 60, 61, 66, 67, 68, 69, 70, 71, 72, 73, 74, 75, 76, 77, 78,79, 80, 81, 82, 83, 84, 85, 86, 87, 88, 92, 93, 94, 95, 96, 97, 98, 99,100, 161, 102, 103, 104, 105, 106, 107, 108, 109, 110, 111, 112, 113,114, 115, 116, 117, 118, 119, 120, 121, 123, 124, 125, 126, 127, 128,129, 130, 131, 132, 133, 134, 135.

[0086] 12) U.S. Pat. No. 5,791,638 Sheets 1, 2, 3, 4, 5, 6, 7, 8, 9, 10,11, 12, 13, 14, 15, 17, 18, 19, 20, 21, 22, 23. FIGS. 1-61 and 66-88 and92-135.

[0087] 13) U.S. Pat. No. 5,709,371, page 1, 2, 3, 4, 5, 6, 7, 8, 9, 10,11, 12, 13, 14, 15, 17, 18, 19, 20, 21, 22, 23. FIGS. 1-61 and 66-88 and92-135.

[0088] The present application which is described in conjunction withTables 1a-1j and Tables 2a-2h.

[0089] The following is a detailed description of this patentapplication. The general description is provided in Tables 1a-1j, Tables2a-2h and FIGS. 1-37.

[0090] Tables 1a-1j Housing Mounted Designs for Holding and OtherApplications

[0091] This consists of 40 different types of grooves and springgeometries in which the spring is mounted in the housing, usingdifferent spring configurations different groove variations, whichdevelop various spring forces and different insertion and runningforces.

[0092] Table 1a-1j

[0093]FIG. 1 shows a flat bottom groove with a radial spring.

[0094] Table 1a, row 2, column 2 shows an assembly with a spring mountedin a housing with a shaft moving back and forth axially.

[0095] Table 1a, row 2, column 3 shows a schematic of the housing.

[0096] Table 1a, row 2 column 4 shows the position of the radial springin a free assembled position and also in the radially spring-loadedposition with the position of the front angle of the spring in relationto the groove.

[0097] Table 1a, row 2, column 5 shows the general dimensions of thecoil width and the coil height with the ID of such spring.

[0098] Table 1a, row 2, column 6 shows the front pictorial view of theradial spring canting counterclockwise.

[0099] Some of the features of these designs are: (1) the groove widthis larger than the coil width. (2) the insertion force will lowerbecause the front angle is the front of the coil. (3) the running axialforce to move the pin forward and back has approximately the samerunning force. This type of gland is relatively easy to fabricate andits geometry allows for large radial spring deflection. The gland canaccommodate different types of spring loads depending on the coil heightand wire diameter and the ratio of the coil height to the wire diameter.The spring can be mounted in the groove clockwise or counterclockwise.The clockwise radial spring has a front angle on the back. (See Table1a, row 2, column 2 and FIGS. 3a; 3 b; 3 c) Counterclockwise radialspring has the front angle in the front. (See FIGS. 2a, 2 b; 2 c). Themain disadvantage of a flat bottom groove is that this spring canshuttle back and forth and in applications involving conductivity, theconductivity is subject to variations due to such shuttling, thuscausing electrical variability.

[0100] Table 1a, row 3 shows the spring mounted 180° from FIG. 1 in aclockwise position.

[0101] Table 1a, row 4, describes a ‘V’ bottom radial spring.

[0102] Table 1a, row 4, column 2 shows a spring mounted in a ‘V’ groovecavity where the pin can and move back and forth axially.

[0103] Table 1a, row 4, column 3 shows a detailed portion of the groove,showing a 30° angle on the groove. The 30° angle has been found to worksatisfactorily. However, other angles may be used ranging from 1° to89°, depending on the application.

[0104] Table 1a, row 4, column 4 shows the spring in a free positionmounted in the groove cavity and also shows the spring coil in a loadedposition. Features of this spring is that the groove width is largerthan the coil width.

[0105] Running forces are generally the same in the backward and forwarddirections.

[0106] Advantages: Reduces spring shuttling.

[0107] Enhances electrical conductivity due to more areas of contact.

[0108] Enhances less electrical variability due to better springretention in the groove.

[0109] Disadvantages:

[0110] Gland is more difficult to fabricate compared to a flat bottomgroove as indicated in Table 1a, row 2, column 3.

[0111] Table 1a, row 4, column 5 shows a cross sectional view showingthe coil heights and coil width and ID of such spring.

[0112] Table 1a, row 4, column 6 shows a pictorial view of a spring in acounterclockwise direction.

[0113] Radial springs can be mounted clockwise or counterclockwise.Counterclockwise springs have the front angle on the front and the backangle on the back. Clockwise radial springs have the front angle on theback and the back angle on the front. (Table 1a, row 3, column 6)

[0114] Table 1a, row 5 describes a Flat bottom axial groove with anaxial RF spring.

[0115] Table 1a, row 5, column 2 shows an assembly view of a spring in aflat bottom groove loaded radially, allowing the spring to assume aconcave position in the initial direction of inserting the pin.

[0116] Table 1a, row 5, column 3 shows a view of the cross section ofthe groove.

[0117] Table 1a, row 5, column 3 shows the spring in an assembledposition with the coils being squeezed axially into the groove. Table1a, row 5, column 4 also shows the spring position after initialinsertion in the initial direction of the pin.

[0118] Features:

[0119] 1) Groove width smaller than the coil height.

[0120] 2) Axial spring being used.

[0121] 3) Variable axial forces. Forward running frictional force isgenerally the same as the backward running force.

[0122] Advantages. Enhanced electrical conductivity is due to morecontact area. Reduced electrical variability due to better retention ofthe spring in the cavity.

[0123] Disadvantages.

[0124] Reduced spring deflection compared to a radial spring.

[0125] Tighter gland width tolerances required.

[0126] Table 1a, row 5, column 5 shows the general dimensions of thecoil and spring with the ID, coil width and coil height.

[0127] Table 1a, row 5, column 6 shows a pictorial view on an RF axialspring.

[0128] Axial springs consist of RF and F springs.

[0129] RF has the coils canting clockwise with the back angle at the IDand the front angle at the O.D. (Table 1a, row 5, column 5 and 6)

[0130] Table 1a, row 6 describes a configuration like the configurationdescribe in Table 1a, row 5 except that an F spring is used instead ofan RF spring.

[0131] F has the coils canting counterclockwise and the back angle onthe OD and the front angle on the ID. (Table 1a, row 6, column 5 and 6)

[0132] Radial springs can be assembled in an axial manner. Table 1b,rows 7, 8, 9 and 10 describe radial springs turned into axial springs

[0133] Table 1b, row 2 describes a flat bottom axial groove with aradial spring mounted into RF position.

[0134] Table 1b, row 2, column 2 shows a radial spring mounted in anaxial manner.

[0135] Table 1b, row 2, column 3 shows a cross section of the groove.

[0136] Table 1b, row 2, column 4 shows the radial spring coil mounted inan axial manner and shown also in a deflected manner.

[0137] Table 1b, row 2, column 5 shows the radial spring dimensionsTable 1b, row 2, column 6 shows a radial spring in a counterclockwisedirection.

[0138] Features:

[0139] (1) The groove width is smaller than the coil height, using aradial spring. (2) Radial spring mounted axially. (3) The forcecharacteristics will be higher than the configuration described in Table1a, row 5, column 6 because the shaft travels against the torsionalforce of the spring as the spring tries to return to its free position.

[0140] Advantages. Enhanced electrical conductivity due to more contactarea. Reduced electrical variability due to better retention of thespring in the cavity.

[0141] Disadvantage. Gland is more difficult to fabricate compared to aflat bottom.

[0142] Tighter gland width tolerances are required.

[0143] Table 1b, rows 3-10 shows the spring mounted in a flat bottomgroove, however, the position that the axial spring assumes after beingassembled in an axial manner is different.

[0144] Table 1b shows a counterclockwise radial spring turned 90°counterclockwise, becoming a counterclockwise F type spring, asindicated in columns 2, 4 and 6.

[0145] Table 1b shows a clockwise radial spring turned 90°counterclockwise, which becomes a clockwise RF spring, as indicated incolumns 2, 4 and 6.

[0146] Table 1b shows a clockwise radial spring turned 90° clockwise,becoming a counterclockwise axial F spring as indicated in columns 2, 4and 6.

[0147] Comparison between counterclockwise radial spring turned 90° intoF and RF springs. See Table 1b, row 2 versus Table 1b, row 3.

[0148] Counterclockwise radial spring turned 90° clockwise intoclockwise axial RF spring and assembled into a groove with the groovewidth less than coil height will yield lower connecting and runningforces compared to the counterclockwise radial spring turned 90° into acounterclockwise axial F spring assembled into the same groove.

[0149] Comparison between clockwise radial spring turned 90° into F andRF axial springs. (See Table 1b, row 4 versus row 5). Clockwise radialspring turned 90° into clockwise RF spring and assembled into an axialgroove (groove width smaller than coil height) will yield lowerconnecting and running forces compared to the clockwise radial springturned 90° into a counterclockwise axial F spring assembled into thesame groove.

[0150] Table 1b, row 6 is a variation of Table 1a, row 5. In Table 1b,row 6 a flat ‘V’ bottom groove is shown, which allows a greater degreeof deflection of the coil. The groove width is smaller than the coilheight, thus assuring retention of the spring. An RF or an F springcould be used in this design. The RF having the front angle on the ODwill have a higher degree of deflection than the F spring that has thefront angle on the OD.

[0151] Table 1c, row 2 shows a variation of Table 1b, row 6. In thiscase, the groove width is larger than the coil height, thus allowing agreater degree of deflection. However, the spring is not firmly retainedin the cavity at assembly.

[0152] Table 1c, row 3 is a variation of Table 1b, row 6. In this case,the groove width is larger than the coil height, thus allowing a greaterdegree of deflection. The design can use an RF, F spring, radial orangular spring. Groove width can also be greater than the coil heightand smaller than the coil width.

[0153] Table 1c, row 4 shows a variation of Table 1a, row 5. In thiscase, a semi tapered bottom groove is shown. The coil width is smallerthan the coil height, thus retaining the spring in place and at the sametime allows a high degree of coil deflection. This particular designallows a greater degree of contact of the coil with the housing, thuspermitting enhanced electrical conductivity and reduced electricalvariability.

[0154] Table 1c, row 6 is a variation of Table 1c, row 5, in which atapered bottom groove is used and the groove width is smaller than thecoil height to facilitate retention of the spring.

[0155] Table 1a, row 5 through Table 1c, row 5 shows the springassembled into the cavity and the pin running in a concave direction.

[0156] Table 1d, row 2 shows a design like Table 1a, row 5, except thatthe pin or shaft has been turned around so that the pin approaches thespring in a convex position. By doing that there is a substantialincrease in the insertion and running forces between the convex andconcave position of the spring coils with the convex position yieldingsubstantially higher running force than moving the pin in a concaveposition. (This is further discussed as shown in FIGS. 16-17). In thiscase, an RF spring is shown.

[0157] Table 1d, row 3 shows the same design as Table 1d, row 2, exceptthat an F spring is shown with a front angle at the inside of the springcoil. In this case, the same as in Table 1d, row 2, the convex insertionand running force is substantially higher than the reverse concaveforce, except that the F spring produces substantially higher insertionand running forces than the RF spring. (Further details will behereinafter discuss in connection with FIGS. 16 and 17 and Table 3)

[0158] Table 1d, row 4 shows a design like Table 1c, row 5 except thatin this case, a spring filled with an elastomer hollow is used.

[0159] Table 1d, row 5 shows a design similar to Table 1d, row 4 exceptthat a spring filled with an elastomer solid is used.

[0160] Table 1e, row 2 shows a variation of the groove in Table 1c, row5 showing a round bottom groove, using an RF spring. The advantage ofthis design is that it provides a concentrated force acting on thespring coil that is desirable in applications where a high stress isneeded to remove oxidation of the coil as it turns, thus enhancingelectrical conductivity and reducing electrical variability.

[0161] Table 1e, row 3 shows a variation of the groove by having atapered groove that can allow the spring to position in one direction orthe other depending on the initial position of the spring duringinsertion.

[0162] Table 1e, row 4 through Table 1f, row 3 shows variations of thedesign in Table 1b, rows 2-5, and in this case, a tapered bottom grooveis used and using a radial spring turned into an axial spring. Thetapered bottom groove allows a higher degree of deflection of the springand allowing a more constant force versus deflection rate than a flatbottom mounted spring.

[0163] Table 1f, row 4 shows a variation of Table 1a, row 2 in which adovetail flat bottom groove is used instead of a flat bottom groove,thus allowing the spring to be retained better in the cavity.

[0164] Table 1f, row 5 shows a variation of Table 1f, row 4 by allowingretention of the spring in a different manner than in FIG. 25 dovetaildesign.

[0165] Table 1g, row 2 is a variation of Table 1a, row 2 and Table 1c,row 3 in which the tapered and flat bottom is shown.

[0166] Table 1g, row 3 shows a variation of the design of Table 1a, row4 with a slight groove configuration but having the V anglesapproximately the same.

[0167] Table 1g, row 4 shows a variation of Table 1g, row 3 in which theV angles are different so that variations in the angle or angles can bemade depending on the application that is intended, thus varying theinsertion and running forces.

[0168] Table 1g, row 4 through Table 1h, row 3 show additionalvariations of the groove depending on the intended purpose that isneeded for the application.

[0169] Table 1h, row 4 through Table 1i, row 4 shows different groovedesigns to suit a specific need. In this case, however, turn anglesprings are being used for the purpose of positioning the spring in sucha manner to facilitate assembly and facilitate position of the spring sothat it can be favorably positioned in applications where the spring isto be located for other subsequent applications, such as locking, and tovary such connecting forces depending on the intended purpose. The turnangles could be anywhere from 1 to 89 degrees, depending on theapplication.

[0170] Table 1i, row 5 through Table 1j, row 3 shows yet anothervariation of the groove cavity to retain the spring in place, dependingon the intended application desirable. The running force may becontrolled by the angles of the groove walls and the positioning of thespring at assembly.

[0171] The various designs indicated in this chart shows an RF spring inpreference to an F spring, primarily because of the higher degree ofdeflection that is available when the front angle is on the outside ofthe coil. However, the F spring could be used in its place whenever ahigher degree of force is desirable with a limited deflection. Also,turn angle springs or different angles may be used ranging from 1 to 89degrees to suit specific applications.

[0172] Piston Mounted Design for Holding and Various Applications(214-28-1).

[0173] Tables 2a through 2h shows 37 variations of the manner in whichthe spring can be mounted in different piston grooves of various designsusing different spring configurations to provide variable insertion andrunning forces. The designs are generally similar to the ones indicatedin Tables 1a-1j, whereby the grooves and designs were housing mounted toapply to those applications where a piston mounted design may bedesirable.

[0174] When mounting the spring into the piston groove—as shown—the backangle of the coil contacts the chamfer of the housing first, uponinsertion.

[0175] Table 2A, row 2 shows a flat bottom groove with acounterclockwise radial spring.

[0176] Table 2a, row 3, column 3 shows a flat bottom groove with aclockwise radially mounted spring with a front angle in a forwarddirection.

[0177] Table 2a, row 2, column 3 shows the general dimensional data forthe groove.

[0178] Table 2a, row 2, column 4 shows the position of the spring priorto connection and after connection, with the back angle coming incontact with the housing during initial connection.

[0179] Table 2a, row 2, column 5 shows the free position of the coil.

[0180] Table 2a, row 2, column 5 shows a radial spring in acounterclockwise direction.

[0181] The forward and backward running force of the pin in the mannerindicated will be approximately the same.

[0182] Shown in Table 2a, row 3 is a design like Table 2a, row 2 exceptthat the spring has been turned around 180° and the pin is moving in thesame direction as in Table 2a, row 2. Under such conditions, theinsertion force will be lower, because the front angle is in the back ofthe coil, while the running frictional force will be about the samegoing forward or backwards. In this case, a radial spring in a clockwisedirection is shown.

[0183] Table 2a, row 4 shows a ‘V’ bottom groove with a counterclockwiseradial spring, which is a variation of the design shown in Table 2a, row2. The ‘V’ bottom groove will reduce spring shuttling and enhanceelectric conductivity. The running force in one direction will beapproximately the same as in the opposite direction.

[0184] Table 2a, row 5 shows a flat bottom axial groove with axialspring with a pin moving forward in a concave direction. The frictionalrunning force in one direction will be similar to the one in the reversedirection. The groove width is smaller than the coil height, thusretaining the spring firmly in place. A spring as mounted will enhanceelectrical conductivity due to greater contact area and also reduceelectrical variability due to better retention of the spring in thecavity. Shown in this case is a RF axial spring.

[0185] Table 2a, row 6 shows a design just like shown in Table 2a, row 5except that it uses an F type spring with a front angle at the inside ofthe spring. F type springs produce substantially higher insertion andrunning forces than RF springs. However, they have lower deflection thanRF spring.

[0186] Tables 2b, rows 2, 3, 4 and 5 show radial springs mounted in aflat bottom groove with the groove width smaller than the coil height.In these cases, a radial spring that can cant clockwise orcounterclockwise has been turned 90° in a clockwise or counterclockwisedirection and assembled into a cavity and retained in such cavity. Undersuch conditions, the insertion and running forces will be substantiallyhigher. This is done in both RF and F springs.

[0187] Table 2b, row 2 shows a flat bottom groove, axial spring withcounterclockwise radial spring mounted in an RF position as indicated inTable 2b, row 2, columns 2-6. The force developed when passing a pistongroove through a housing with a spring turned from a radial to an axialposition will be substantially higher than a comparable RF spring asindicated in Table 2a, row 5 due to the torsional force placed on thespring during insertion into the axial cavity. In this case, acounterclockwise spring is turned 90° into a clockwise axial RF springand assembled into an axial groove cavity with the groove width smallerthan the coil height.

[0188] Table 2b, row 3 is like Table 2b, row 2 except that an F springhas been mounted in the cavity. The radial spring turns counterclockwiseand is turned 90° to assume an axial counterclockwise spring F type andassembled into the cavity.

[0189] Comparison between clockwise radial spring turned 90° into F/RFsprings.

[0190] Table 2b, row 2, column 6 versus Table 2b, row 3, column 6.Counterclockwise radial spring turned 90° into a clockwise axial RFspring and assembled into a groove with the groove width smaller thanthe coil height, will yield lower connecting and running forces comparedto the counterclockwise radial spring turned 90° into a counterclockwiseaxial F spring assembled in the same groove.

[0191] The running force in a concave and convex direction will be aboutthe same.

[0192] Table 2b, row 4 shows the same design as in Table 2b, rows 2 and3 except that in this case a radial clockwise spring has been turnedinto an RF clockwise axial spring by turning it 90°.

[0193] Table 2b, row 5 is a design similar to Table 2b, row 4 and inthis case the clockwise canting coil spring has been turned 90° into ancounterclockwise axial F type spring and assembled into a cavity whosegroove width is smaller than the coil height.

[0194] Comparison between clockwise radial spring turned 90° into an RFand F axial spring. (See Table 2b, row 4, column 6 versus Table 2b, row6, column 6). Clockwise radial spring turned 90° into a clockwise axialRF spring and assembled into an axial groove with GW smaller than coilheight will yield lower connecting and running forces compared to theclockwise radial spring turned 90° into a counterclockwise axial Fspring assembled into the same groove.

[0195] Table 2b, row 6 shows a variation of the design indicated inTable 2a, row 5. In this case a ‘V’ bottom groove is used that willprovide a higher degree of deflection than that can be obtained in FIG.4 and such deflection will be more uniform. Groove width is smaller thanthe coil height.

[0196] Table 2c, row 2 is a variation of Table 2b, row 4 with the groovewidth larger than the coil height and providing higher deflection butless retention capabilities in the groove.

[0197] Table 2c, row 3 shows a ‘V’ bottom groove with an axial springwith a groove width larger than the coil height. The design is similarto Table 2b, row 6 except that the spring is not retained in the cavityaxially, like Table 2b, row 6. In this case, an RF spring is shown butcan use a F, radial or angular spring. Groove width can also be largerthan the coil height and smaller than the coil width.

[0198] Table 2c, row 4 shows a semi-tapered groove with an RF axialspring.

[0199] Table 2c, row 5 shows a tapered bottom groove with an RF axialspring.

[0200] Table 2a, row 5 through Table 2c, row 5 use axial springs. Suchsprings can be F or RF or could be radial turned into axial.

[0201] Table 2c, row 6 shows a tapered bottom groove with an axial RFspring with a shaft that travels in a convex direction, which is 180°from the one shown in Table 2c, row 5. When the piston groove travels ina convex direction, the insertion and running forces are substantiallyhigher than when the spring travels in a concave direction and anequivalent description of this feature is also indicated in FIGS. 16-17.In this case, an RF spring is being used.

[0202] Table 2d, row 2 shows a tapered bottom groove with an axial Fspring that travels in a convex direction with the groove width smallerthan the coil height. The groove configuration is the same as in Table2c, row 6 except that the spring is an F spring instead of an RF spring.The force in a convex direction is substantially higher than a concavedirection and the F spring always provides a higher insertion andrunning force than an RF spring due to the fact that the back angle isin the OD resulting in substantially lower deflection and higher force.

[0203] Table 2d, row 3 is a tapered bottom groove with an RF axialspring filled with an elastomer hollow. This design is similar to Table2c, row 4 except that the spring is filled with an elastomer hollow.

[0204] Table 2d, row 4 is a tapered bottom groove with an RF axialspring filled with an elastomer solid. The design is similar to Table2c, row 4 except that the spring is filled with an elastomer solid.

[0205] Table 2d, row 5 shows a round flat bottom groove with an RF axialspring. This type of design provides a higher stress concentration atone point to scrape oxidation of the spring coil.

[0206] Table 2e, row 2 shows an inverted ‘V’ bottom grove with an RFaxial spring that can be moved in a concave or convex direction,depending on the initial movement of the piston groove. In this case, anRF spring is being used.

[0207] Table 2e, row 3 through row 6 shows a radial spring turned intoan axial spring and inserted in an axial cavity.

[0208] Table 2e, row 3 shows a tapered bottom groove with a radialcounterclockwise radial spring mounted in RF position with a groovewidth smaller than the coil height. In this case, a clockwise spring hasbeen turned 90° into an axial RF spring and inserted into the cavity.

[0209] Table 2e, row 4 shows a counterclockwise radial spring turnedinto an axial F counterclockwise spring.

[0210] Table 2e, row 5 shows a clockwise radial spring turned into an RFclockwise spring.

[0211] Table 2e, row 6 shows a clockwise radial spring turned into axialF spring.

[0212] All axial springs can be used in F or RF and radial springs canbe turned into axial springs by turning such springs 90° clockwise orcounterclockwise and assembling into a cavity whose groove width issmaller than the coil height.

[0213] Table 2f, row 2 shows a dovetail groove with clockwise radialspring with a groove width larger than the coil width. The design issimilar to FIG. 1 except that the spring is better retained in thecavity.

[0214] Table 2f, row 3 shows a dovetail groove with clockwise radialspring, which is a variation of Table 2f, row 2.

[0215] Table 2f, rows 4-6 and Table 2g, rows 2-4 shows differentvariations of the groove using a radial spring mounted into such groove.The springs are shown in a counterclockwise mounting direction.

[0216] Table 2g, rows 5-6 and Table 2h, rows 2-4 shows variations ofdifferent types of grooves using a turn angle spring to achieve specificgoals such as to vary the initial insertion force to increase ordecrease disconnect force as a subsequent step to enhance conductivity,reduce variability, or enhance areas of contact for better reliability.

[0217] Classification of design features and characteristics of holdingconnectors using the canted coil springs.

[0218]FIGS. 1-37 provide a greater detailed data on the different grooveconfigurations, different types of springs, running forces andbackground information on the different features of connectors, forceparameters, and unique features of such connectors as related to thispatent application.

[0219]FIGS. 1a, 1 b, 1 c, 1 d, and 1 e, show a description of the frontand back angles of the canted coil spring with the following features.

[0220] A canted coil spring consists of two halves. One-half is theshorter back angle half of the coil and the other is the longer frontangle half coil. The front angle half is longer (See FIG. 1d) and itslever arm is larger (1 e), thus less force is needed to deflect suchspring compared to the back angle half coil.

[0221]FIGS. 1a, 1 b, 1 c, 1 d, and 1 e describe the different positionsof a radial spring and the front and back angle.

[0222]FIG. 1

[0223] Definitions as apply to this patent application:

[0224] (A) Shaft connecting-insertion force is the force required toinsert the chamfer part of the shaft through the ID of the spring untilthe ID makes contact with the body of the shaft where the diameter isconstant. (See FIGS. 2c, 3 c)

[0225] (B) Housing connecting insertion force is the force required toinsert the piston through the chamfer portion of the housing. (See Table2a, row 2, columns 2 and 4)

[0226] (C) Running force is the force of the shaft is the force requiredto move the body of the shaft (constant diameter part) through the ID ofthe spring after it has been connected.

[0227] (D) Running force of the piston is the force required to move thepiston through the bore (constant diameter part)

[0228] Radial springs. Radial springs are divided into clockwise andcounterclockwise springs.

[0229] Counterclockwise spring has the front angle in the front. Theweld reference point is also in the front angle facing the incomingmotion of the shaft. In the case of a housing, the counterclockwisefront angle is in the back of the coil (Table 2a, row 2, column 2).

[0230] Counterclockwise radial spring is the same as a clockwise radialspring except that it is turned 180°. The running force of a radialspring mounted on a flat bottom groove canting clockwise orcounterclockwise is about the same. Counterclockwise radial springs aredescribed in FIG. 2a, FIG. 2b, and FIG. 2c.

[0231]FIG. 2 Counterclockwise Radial Spring in Flat Bottom HousingGroove

[0232] Counterclockwise radial springs are described in FIG. 2a, FIG.2b, and FIG. 2c.

[0233] The front angle is in the front facing the incoming motion of theshaft. In the case of the piston (Table 2e, row 3, column 3) the backangle faces the incoming motion of the piston.

[0234] The running force developed when the shaft travels against radialsprings mounted counterclockwise (FIG. 2c), similar to the running forcedeveloped when the shaft travels against radial springs mountedclockwise (FIG. 3c)

[0235]FIG. 3. Clockwise radial spring and flat bottom housing groove,front angle in the back.

[0236] Features

[0237] The back angle is in the front, the weld referenced point is inthe back facing away from the incoming motion of the shaft or bore. Aclockwise radial spring is the same as a counterclockwise radial springexcept that it is turned 180°. The running force of a radial springmounted in a flat bottom housing groove canting clockwise orcounterclockwise is about the same.

[0238]FIGS. 3a, 3 b, and 3 c describe a clockwise radial spring andmounting means in a flat bottom groove.

[0239] There is no significant variation in running force when movingthe shaft with the spring mounted in a counterclockwise or clockwiseposition.

[0240]FIG. 4 shows a RF clockwise axial spring in a tapered bottomgroove. The shaft travels forward in a concave position as shown in FIG.4c direction in respect to the ID of the spring.

[0241]FIG. 5 shows an RF spring clockwise axial spring mounted in atapered bottom groove, housing groove, shaft travels backward in theconvex direction. Direction with respect to the spring ID.

[0242] Comparing FIGS. 4a, 4 b, 4 c, and 4 d with 5 a, 5 b, 5 c, and 5 dshows that the running force in a concave direction and the runningforce in a convex direction is approximately the same.

[0243]FIGS. 6 and 7 shows the same type of design (FIG. 6c and FIG. 7c)with the spring mounted in a piston. The results are in essence thesame, that is, the running force in a concave direction is essentiallythe same as the convex direction running backwards using an RF springwith the results being similar to those indicated when the spring ismounted in the housing.

[0244]FIGS. 8 and 9 make a comparison similar to those indicated inFIGS. 4 and 5 but in this case an F axial spring is being used. Theresults show that when an F spring is mounted in a housing and theconcave and convex direction is measured, going forward and back, theconvex direction develops approximately 7% greater force than theconcave direction, indicating that the F springs with lower deflectionand higher force per unit deflection develops a higher differentialrunning force than an equivalent RF spring by approximately 18% to 25%.

[0245]FIGS. 10 and 11 shows an F spring mounted in a piston and theresults also indicate that when a F spring is mounted in a piston andmoved forward in a concave direction, it develops lower force than whenmoving the same piston backwards in a convex direction. The variation isapproximately 7% with a convex movement developing higher force.

[0246]FIG. 12. Counterclockwise radial spring turned 90°counterclockwise into a counterclockwise axial F spring and assembled ina groove with groove width smaller than the coil height. This isdescribed in FIGS. 12a through 12 g. Comparing an axial spring asindicated in FIGS. 8a, 8 b, and 8 c and compared to that of 12 a through12 g shows that when a radial spring has been turned 90° into an axialspring and assembled into a groove, the coils have higher stress levelcompared to an axial F spring in the same groove. This added stressdevelops higher running force.

[0247] Another factor that affects running force is when the shafttravels in a concave direction. The friction between the shaft andspring turns the spring clockwise, opposing the natural tendency of thespring as its torsional force tries to return the spring to its built-inradial position by turning counterclockwise. The combination ofpre-stress torsional force direction and position of the back angle atthe OD gives this design 12-c about 10 to 30 percent higher runningforce compared to the design in FIG. 8c.

[0248]FIG. 13. Counterclockwise radial spring turned 90° clockwise intoa clockwise axial RF spring assembled in a groove with a groove widthsmaller than the coil height.

[0249]FIGS. 13a through 13 g describe this spring. It has been turnedfrom a radial counterclockwise spring into an axial RF spring. Comparing13 g to 4 c it shows that when a radial spring has been turned 90° intoan axial spring and assembled into a groove, the coils have a higherstress level compared to an axial RF spring in the same groove. Thisadded stress develops higher running force. Another factor that affectsthe running force is when the shaft travels in a concave direction. Thefriction between the shaft and spring turns the spring clockwise,assisting the natural tendency of the spring as its torsional forcetries to return the spring to its built-in radial position by turningclockwise. The combination of pre-stress torsional force direction andposition of the back angle at the ID gives the design 13 c about 10 to20 percent higher running force compared to the design in FIG. 4c.

[0250]FIG. 14. Clockwise radial spring turned 90° counterclockwise intoa clockwise axial RF spring and assembled in a groove with a groovewidth smaller than the coil height. Comparing FIG. 14g with 4 c it showsthat the combination of pre-stress torsional force and position of theback angle at the ID gives this design 14 g about 10 to 20 percenthigher running force compared to the design in 4 c.

[0251]FIG. 15 clockwise radial spring turned 90° clockwise into acounterclockwise axial F spring and assembled in a groove with groovewidth smaller than the coil height. FIGS. 15a through 15 g describe thistype of spring and when we compare FIG. 15g to 8 c it shows that thecombination of pre-stress torsional force direction and position of theback angle at the OD gives this design (FIG. 15c) about 10 to 30 percenthigher running force compared to the design in FIG. 8c.

[0252]FIG. 16 and FIG. 17.

[0253]FIG. 16. Axial RF and F springs show a shaft moving in the concavedirection of the spring ID as shown in FIG. 16a and FIG. 16b and FIG. 17showing an axial RF and F spring shaft moves in the convex direction ofthe spring ID as shown in FIG. 17a and FIG. 17b. In this case, acomparison has been made between the direction of motion in a concavedirection as indicated in FIGS. 16a and 16 b with that of FIGS. 17a and17 b. The results show that for both RF and F springs when the pin orshaft moves in a concave direction it provides substantially lower forcethan when the same pin is turned around 180° and move the pin in aconvex direction with the RF springs developing substantially lowerforce than the F springs. See Table 3 for results and Table 4 forspring/groove specifications.

[0254] The unexpected results show as follows:

[0255] RF spring. Running Force. The running force of the shafttraveling in the convex direction is 304% higher than the running forceof the shaft traveling in the concave direction.

[0256] F spring. Running Force: The running force of the shaft travelingin the convex direction is 1233% higher than the running force of theshaft traveling in the concave direction.

CONCLUSION

[0257] The running force difference between the shaft traveling in theconcave and convex direction is substantial. When the shaft travels inthe convex direction, the insertion and running forces are higher inboth RF and F axial springs. In RF springs the increase in running forcewas 304%. In F spring the increase was 1233%.

[0258] The substantially higher force when the shaft is inserted andtraveled in the convex direction occurs because during insertion, theshaft's chamfer turns the spring clockwise, as the spring turnsclockwise, the point of contact between the shaft and the spring movescloser to the centerline of the major axis where no spring deflection ispossible. Large amount of force is required to force the chamfer part ofthe shaft to pass the spring. After the shaft has been inserted and thespring has wedged against the shaft, the shaft continues to travel inthe same direction, the friction between the spring and the shaft turnsthe spring clockwise opposing the natural tendency of the spring as ittries to deflect. The action keeps the spring in the wedged position andtherefore a large amount of force is required for the shaft to travel inthe convex position after it has been inserted in the same direction(FIG. 17a and FIG. 17b).

[0259] The ‘F’ springs in the convex direction produces substantiallyhigher running force 1233% than ‘F’ springs in the concave direction. In‘RF’ springs, the running force in the convex direction is 304% higherthan in the concave direction.

[0260] Values vary depending on various parameters such as groovedimensions, spring dimensions and piston/shaft dimensions, etc.

[0261]FIGS. 18 and 19. Reviewing FIGS. 18 and 19 when the pin moves awayfrom a turn angle ‘a’ the running force developed is substantially lessthan when the pin moves towards the tapered angle ‘a’. In both cases,the spring turns clockwise.

[0262]FIGS. 20 and 21. Radial springs. OD of radial spring is largerthan the ID of the housing spring mounted in the housing. This isdescribed in FIGS. 20a, 20 b, and 20 c in which it shows that the OD ofthe spring is larger than the ID of the cavity in which such spring isto fit. Compressing the spring from the OD results in an increase in theback and front angles of the coil and thus reducing the insertion andrunning forces.

[0263]FIG. 21 radial spring. OD of radial spring is the same as the ODof the housing spring mounted in the housing.

[0264]FIGS. 21a, 21 b, and 21 c shows that the ID of the spring issmaller than the shaft diameter, thus requiring stretching of thespring. In stretching the spring from the ID results in a decrease inthe front and back angle, resulting in higher insertion and runningfrictional forces.

[0265] Table 5 makes a comparison between springs having differentsprings ID and OD and assembled into the same cavity having the sameshaft and same housing. The results shows that the stretching the springfrom the ID results in higher running force. Compressing the spring fromthe OD results in lower running force.

[0266]FIG. 22. Radial spring. Spring mounted on the piston, spring ID issmaller than the piston groove diameter indicated in FIGS. 22a and 22 b.In this case, by stretching the spring to mount in a groove or pistonresults in higher running force.

[0267]FIG. 23. Radial spring. Spring mounted on the piston. Spring ID isequal to the piston groove diameter.

[0268]FIG. 23a, FIG. 23b, and FIG. 23c. In this case, the spring ID isequal to the piston groove diameter but the spring OD is larger than thehousing diameter. The results show that by compressing the coils fromthe OD of the spring it increases the front and back angles, resultingin lower breakout and running forces.

[0269]FIG. 24. Same shaft diameter, same spring diameter, varyinghousing bore diameter. This is indicated in FIG. 24 in which it shows anassembly with the same shaft diameter and the same spring with differenthousing diameters. Compressing the spring coils from the OD results inlower running frictional forces than compressing the coils from the ID.The reason being is that when compressing the coil from the OD itincreases the front and back angle, decreasing the force required topass a plunger through such spring ID.

[0270]FIG. 25. Same housing bore diameter, same spring diameter, bearingshaft diameter. FIG. 25 shows an assembly having a constant borediameter, a constant spring diameter, and a variable shaft diameter. Theresults, as indicated, in Table 6 comparing the running force of aspring compressed from the OD at various deflections shows thatcompressing the coils from the OD while maintaining the same spring andshaft diameter results in lower running force.

[0271] Table 7 compares running force of a spring compressed from the IDat various deflections and it shows that stretching the spring ID to theshaft diameter and compressing the coils from the ID results in higherrunning force. Stretching the spring increases the deflection beforebutting.

[0272]FIG. 26. F spring vs. RF spring mounted in a housing. FIG. 26a andFIG. 26b makes a comparison between an RF spring mounted in the samehousing versus an F spring mounted in the same housing. The RF springhas the front angle on the OD while the F spring has a front angle atthe ID. The results, as indicated in Table 8 shows that RF springsdevelop 10 to 20 percent lower running force than F springs under thesame conditions.

[0273] The results show then that an F series spring develops higherrunning force than RF series. The average running force of the RFsprings is 10% to 20% lower compared to the average running force of theF spring, depending on the spring series. Table 8 compares the runningforce of F springs mounted in a housing. RF springs develop 10 to 20percent lower running force than F springs under the same conditions.Table 8 shows a variation of approximately 10% lower for the RF springs.Values vary substantially with the spring and groove parameters.

[0274]FIG. 27. F spring versus RF spring mounted on a piston

[0275]FIG. 27a shows a RF spring mounted on a tapered bottom piston withthe front angle at the OD and the back angle at the ID.

[0276]FIG. 27b shows the same type of design except that in this case,an F spring is shown with the front angle at the ID and the back angleat the OD. The spring is assembled in the cavity having a groove widthsmaller than the coil height and assuming a vertical position. Uponassembling the piston into the housing, the spring assumes a concaveposition, and the running force of the RF spring is lower than the forceof the F spring, changing from approximately 10% to 30% lower. Table 9shows a variation of approximately 16% lower for the RF springs. Valuesvary substantially with the spring and groove parameters.

[0277]FIG. 28 shows a variation of the RF spring diameter and its effecton forces.

[0278]FIG. 28a shows axial springs of different diameters with thesmaller diameter equal to the shaft diameter. Other springs having alarger ID when assembled into the housing whose groove width is smallerthan the coil height. Upon assembling such springs into the same cavity,as indicated in FIG. 28c, the spring coils assume a position asindicated in FIG. 28f, and the springs having a larger inside diameterand a larger outside diameter and therefore more coils per spring, whencompressed radially by reducing the outside diameter, causes the backangle and front angle to increase, decreasing the force required to passa plunger through the ID of such spring. The results, as indicated inTable 10 Axial RF Spring Versus Running Force, show that the largerdiameter springs with more coils develop lower force than the springswith fewer number of coils and having a smaller inside and outsidediameter. The variation can range anywhere from 10 to 30 percent or moredepending on spring and groove parameter.

[0279]FIG. 29 compares the variation of an F spring diameter and itseffect on force.

[0280]FIGS. 29a, 29 b, and 29 c are the same as in FIG. 28, except thatan F spring instead of an RF spring is being used; the F spring havingthe front angle at the ID and the back angle at the OD. The results, asindicated in Table 11, show that the springs with the larger outsidediameter and thus a larger number of coils when compressed into ahousing, as indicated in FIG. 29b, show that the larger diameter springswhen the pin is passed through the ID of such spring develop asubstantially lower force than the smaller diameter springs, asindicated in Table 11. The variation ranges from approximately 10 to 30percent and such variations depend on groove and spring considerations.

[0281] Comparing the running forces between the RF and F springsindicated in FIGS. 28b and 29 b as recorded in Table 10 and 11, it showsthat F springs under the same conditions develop higher running forcesthan RF springs.

[0282] FIGS. 30 to 37 shows different kinds of groove springconfigurations having a flat bottom groove, both on the housing and inthe piston using axial springs in a groove whose groove width is smallerthan the coil height.

[0283]FIGS. 30 and 31 makes a comparison between the force developedwhen passing a pin in a concave and a convex direction. In this case,when using an RF spring, the running force back and forth is essentiallythe same in both cases.

[0284]FIGS. 32 and 33 shows design where the spring is mounted in apiston groove with the front angle on the OD and the back angle on theID. In this case, the springs are also positioned in a concave positionand when moving the pin in a concave direction or in a convex direction,the running force is essentially the same in one direction or the other.

[0285]FIGS. 34 and 35 shows an F spring mounted in a housing and the pinmoving in a concave direction and also in a convex direction. In thiscase, when the pin is moved in a convex direction, the running forcewith the F type spring runs approximately 10 to 30 percent higher thanwhen running in a concave direction. The variation depends on the grooveconfiguration and spring design.

[0286]FIGS. 36 and 37 also makes a comparison between a F spring mountedin a piston groove and the pin moving in a concave or convex direction.When the pin is moved in a convex direction, the frictional forcedeveloped is anywhere from 10 to 30 percent higher than when moving in aconcave direction.

[0287] A review of the results indicated in FIGS. 30 to 37 indicatesthat when using the RF spring, having a front angle on the OD and theback angle on the ID, the force versus deflection remains much moreconstant than when using an F spring that has substantially lowerdeflection and a higher force versus deflection; thus, a small amount ofdeflection results in a substantially higher force and is represented bythe values indicated, whereby when using the F spring the insertion andrunning forces are substantially higher than those obtained with an RFspring.

[0288] The springs herein shown illustrate circular springs that canradial, axial or turn angle, that can be joined in various ways,primarily by bringing the ends together by welding, thus forming acircle. However, such springs can also be held together in many otherways and still permit the operational requirements as indicated.

[0289] The springs can be mounted in a housing groove or can be mountedin a piston groove and the springs can be radial and mounted radially;can be radial and mounted axially and can be axial and mounted axiallyand the springs can also be turn angle and they can be mounted radiallyor axially.

[0290] Housing mounted springs. The housing mounted springs can beassembled into a groove in the following manner.

[0291] 1. By making the length of the spring longer than the length ofthe circumference that the groove in which it is to fit so that the endsof the spring can be encased into the ends of such coils in a radial,axial or turn angle manner.

[0292] 2. By making the length of the spring slightly longer than thelength of the circumference of the groove so that upon assembling intothe housing the ends of the spring will come in contact with each other,due to the longer length of the spring over the length of the cavity.

[0293] 3. By making the length of the spring shorter than the length ofthe circumference of the groove in which it is to fit in so that uponassembly there will be a gap between the ends of the coils, onceassembled into the cavity.

[0294] Piston mounted springs. The piston mounted springs will be madein a similar manner as the ones that are mounted in the housing asfollows:

[0295] 1. Making the length of the spring larger than the internalgroove length of the cavity so that the ends of the coils are encasedinto each other, be radial or axial or turn angle.

[0296] 2. By making the length of the spring slightly larger than thelength of the circumference of the piston groove so that upon assembly,the ends of the coil will be butting against each other.

[0297] 3. By making the length of the spring smaller than the length ofthe circumference of the piston groove so that upon assembly there willbe a gap between the coils.

[0298] The springs can be radial and upon assembly, they can cantclockwise or counterclockwise. The springs can also be axial wherebyupon assembly they will be RF with a front angle on the OD or F with thefront angle on the ID.

[0299] The length of the springs can be assembled in the housing or inthe piston as indicated in U.S. Pat. No. 5,709,371, U.S. Pat. No.5,791,638 and U.S. Pat. No. 5,615,870 all to Bal Seal.

[0300] The conductivity/resistivity and the variability of the currentpassing from the housing to the shaft through the spring or vice versais affected by various parameters, which are as follows:

[0301] The method of mounting the spring in the housing, be it a radialor axial spring. An axial spring or a radial spring mounted axially willdevelop higher stress on the shaft than an equivalent radial spring.

[0302] An F spring will develop a higher stress on the shaft than anequivalent RF spring.

[0303] The smaller the ratio of the spring ID to the coil height, thehigher the stress acting on the coils at the ID and the higher thestress acting on the shaft.

[0304] The smaller the ratio of the spring ID to the ratio of the coilheight to wire diameter, the higher the stress acting on the coils atthe ID and the higher the stress acting on the shaft. The resistivityand conductivity is affected to a certain extent by the stress in poundsper square inch acting on the shaft. Such stress is not linear, meaningthat after a certain amount of stress an increase in stress does notresult in an increase in conductivity. However, the variability of theresistivity is reduced by higher stress acting on the shaft. The higherthe eccentricity and angular misalignment, the higher the variabilitythat can occur. Therefore, the most desirable condition occurs when weobtain maximum deflection of the spring coils as well as adequate stressof those coils. The higher deflection of the spring at the ID of suchspring will permit a higher degree of eccentricity, angularmisalignment, and tolerance variation of the pin. For example, Table 1a,row 2, column 2, 3 and 4, show a radial spring mounted in a housing anddeveloping a minimum amount of stress acting on the shaft, but a highdegree of deflection of the coil. On the other hand, row 5, column 2,uses an axial spring with a flat bottom groove that develops a highlevel of stress on the pin but a lower ability to accommodateeccentricities, misalignment and tolerances than Table 1a, row 2,columns 2, 3, and 4.

[0305] On the other hand, row 5, column 2 and 3 of Table 1a, with anaxial spring having a tapered bottom groove provides slightly lowerstress than row 5, column 2, row 6, column 2 of Table 1a, but a higherdegree of deflection at the coil ID that can accommodate bettertolerance variations, eccentricities and angular misalignment of thecoil, thus affecting electrical resistivity. In addition, the type ofaxial spring being an RF or F affects the stress acting on the pin aswell as ability to accommodate eccentricities, tolerance variations, andangular misalignment of the pin. The RF spring provides lower stress buta greater ability to accommodate for tolerances, misalignment andeccentricity. These variations affect the selection of the spring,either radial or axial and the type of radial spring and the type ofgroove design. It has been discovered that for most general applicationswhere resistivity and resistivity variability is to be kept at aminimum, the design indicated in FIG. 14A Chart I, with the taperedbottom groove having a front angle on the OD offers the best combinationof properties in holding applications. Whenever a high degree of stressis indicated with limited radial variation, the design indicated in row5, Table 1a, combines such properties. The designs indicated in rows 2,3 and 4 of Table 1a, provide limited stress on the pin but the forcevariability during axial movement of the pin is substantially moreconstant.

[0306] Although there has been hereinabove described specific springholding connectors in accordance with the present invention for thepurpose of illustrating the manner in which the invention may be used toadvantage, it should be appreciated that the invention is not limitedthereto. That is, the present invention may suitably comprise, consistof, or consist essentially of the recited elements. Further, theinvention illustratively disclosed herein suitably may be practiced inthe absence of any element which is not specifically disclosed herein.Accordingly, any and all modifications, variations or equivalentarrangements which may occur to those skilled in the art, should beconsidered to be within the scope of the present invention as defined inthe appended claims.

TABLE 3 Running Force Comparison: Shaft Inserted in the ConcaveDirection vs. Shaft Inserted in the Convex Direction for Axial F and RFSprings. RFX37367 RFX37367 FX37367 FX37367 Running Running RunningRunning Force in Force in Percent Force in Force in Percent The TheDifference The The Difference Concave Convex in Concave Convex inDirection Direction Running Direction Direction Running Item# (lbs)(lbs) Force % (lbs) (lbs) Force % 1 0.24 0.61 0.27 2.56 2 0.23 0.59 0.272.50 3 0.24 0.55 0.27 2.39 4 0.21 3.19 0.26 6.20 5 0.21 0.36 0.26 6.11 60.20 0.35 0.26 4.74 7 0.23 1.57 0.27 2.93 8 0.22 0.45 0.30 2.64 9 0.230.43 0.28 2.47 Average: 0.222 0.898 304 0.271 3.614 1233

[0307]

TABLE 5 Running Force Comparison of Springs with Various ID Mounted on aHousing % of Change in Shaft Bore Average Test Spring Spring DiameterDiameter Running Running Number Spring ID (in) OD (in) (in) (in)Force(g) Force 1 104LB-(.341) 0.341 0.513 0.371 0.498 165 104LB-(.341)0.341 0.513 0.371 0.498 165 104LB-(.341) 0.341 0.513 0.371 0.498 170104LB-(.341) 0.341 0.513 0.371 0.498 170 104LB-(.341) 0.341 0.513 0.3710.498 161 Average 166 BASE 2 104LB-(.518) 0.518 0.690 0.371 0.498 121104LB-(.518) 0.518 0.690 0.371 0.498 101 104LB-(.518) 0.518 0.690 0.3710.498 124 104LB-(.518) 0.518 0.690 0.371 0.498 120 104LB-(.518) 0.5180.690 0.371 0.498 121 Average 117 −29 3 104LB-(.550) 0.550 0.722 0.3710.498 112 104LB-(.550) 0.550 0.722 0.371 0.498 114 104LB-(.550) 0.5500.722 0.371 0.498 114 104LB-(.550) 0.550 0.722 0.371 0.498 113104LB-(.550) 0.550 0.722 0.371 0.498 103 Average 111 −33

[0308] TABLE 6 Running Force of Springs Compressed from the OD atVarious Deflection Shaft Bore Perc nt Defl ction (%) Test NumberDiameters Diameters Running Friction Forces (g) No. Springs of Coils(in) (in) 10% 17% 25% 35% 1 104MB(0.125)- 27 0.125 0.273, 0.263, 179 233359 1288 SS-SOW 0.249, 0.233 (butting) 2 104MB(0.250)- 44 0.250 0.398,0.388, 343 422 479 2912 SS-SOW 0.374, 0.358 (butting) 3 104MB(0.500)- 740.500 0.648, 0.638, 570 679 705 1302 SS-SOW 0.624, 0.608 (butting) 4104MB(1.000)- 143 1 1.148, 1.138, 1160 1361 1528 2523 SS-SOW 1.124,1.108 (butting)

[0309] TABLE 7 Running Force of Springs Compressed from the ID atVarious Deflection Bore Percent Deflection (%) Test Number DiametersRunning Friction Forces (g) No. Springs of Coils Shaft Diameters (in)(in) 10% 17% 25% 35% 1 104MB(0.125)- 27 0.143, 0.153, 0.167, 0.291 324315 389 442 SS-SOW 0.183 2 104MB(0.250)- 44 0.268, 0.278, 0.292, 0.3080.416 368 382 541 594 SS-SOW 3 104MB(0.500)- 74 0.518, 0.528, 0.542,0.666 814 871 901 979 SS-SOW 0.558 4 104MB(1.000)- 143 1.018, 1.028,1.042, 1.058 1,166 1433 1473 1768 1683 SS-SOW

[0310] TABLE 8 Running Force of RF Springs vs. Running Force of FSprings Mounted in a Housing Number Average % of Change Spring SpringSpring of Coils % of Running in Average No. Series ID (in) per SpringDeflection Force (g) Running Force 1 F104MC 0.625 85 25 722 2 F104MC0.625 85 25 643 3 F104MC 0.625 85 25 694 Average 686 BASE 1 RF104MC0.625 85 25 639 2 RF104MC 0.625 85 25 652 3 RF104MC 0.625 85 25 555Average 615 −10

[0311] TABLE 9 Running Force of RF Springs vs. Running Force of FSprings Mounted in a Piston % of Number Change in of Coils AverageAverage Spring Spring Spring per % of Running Running No. Series ID (in)Spring Deflection Force (g) Force 1 F104MC 0.625 85 25 612 2 F104MC0.625 85 25 585 3 F104MC 0.625 85 25 626 4 F104MC 0.625 85 25 594 5F104MC 0.625 85 25 585 Average 601 BASE 1 RF104MC 0.625 85 25 452 2RF104MC 0.625 85 25 562 3 RF104MC 0.625 85 25 465 4 RF104MC 0.625 85 25525 5 RF104MC 0.625 85 25 505 Average 502 −16

[0312] TABLE 10 Axial RF Spring Diameters vs. Running Force Number ofAverage % of Change in Spring Spring Spring Coils per % of RunningAverage No. ID (in) Series Spring Deflection Force (g) Running Force 10.625 RF104MC 85 25 683 2 0.625 RF104MC 85 25 675 3 0.625 RF104MC 85 25590 4 0.625 RF104MC 85 25 677 5 0.625 RF104MC 85 25 613 Average 648 BASE1 0.650 RF104MC 88 25 628 2 0.650 RF104MC 88 25 557 2 0.650 RF104MC 8825 561 4 0.650 RF104MC 88 25 559 5 0.650 RF104MC 88 25 551 Average 571−12 1 0.675 RF104MC 91 25 538 2 0.675 RF104MC 91 25 544 3 0.675 RF104MC91 25 536 4 0.675 RF104MC 91 25 621 5 0.675 RF104MC 91 25 582 Average564 −13

[0313] TABLE 11 Axial RF Spring Diameters vs. Running Force Number ofAverage % of Change Spring Spring Spring Coils per % of Running inAverage No. ID (in) Series Spring Deflection Force (g) Running Force 10.625 F104MC 85 25 720 2 0.625 F104MC 85 25 695 3 0.625 F104MC 85 25 6904 0.625 F104MC 85 25 760 5 0.625 F104MC 85 25 725 Average 718 BASE 10.650 F104MC 88 25 625 2 0.650 F104MC 88 25 620 3 0.650 F104MC 88 25 6254 0.650 F104MC 88 25 600 5 0.650 F104MC 88 25 625 Average 619 −14 10.675 F104MC 91 25 585 2 0.675 F104MC 91 25 610 3 0.675 F104MC 91 25 6254 0.675 F104MC 91 25 540 5 0.675 F104MC 91 25 570 Average 586 −18

What is claimed is:
 1. A spring holding connector comprising: a housinghaving a bore therethrough; a shaft rotatably and slidably received insaid bore; a circular groove formed in one of said bore and shaft; acircular spring disposed in said groove for slidably holding said shaftwithin said bore; said groove being sized and shaped for controlling, incombination with a spring configuration, shaft mobility within saidbore.
 2. The connector according to claim 1 wherein said spring isturnable in said groove for causing forces required to move the shaftwithin said bore to be dependent upon a direction of the movement. 3.The connector according to claim 1 wherein said spring is compressiblein said groove for causing forces required to move the shaft within saidbore to be dependent upon a direction of the movement.
 4. The connectoraccording to claim 2 wherein the movement is axial.
 5. The connectoraccording to claim 3 wherein the movement is axial.
 6. The connectoraccording to claim 1 wherein said spring is turnable in said groove forenhancing electrical conductivity between said shaft and said housing byremoving oxidation on said spring.
 7. The connector according to claim 6wherein said groove includes an uneven bottom for scraping said springas said spring turns therepast.
 8. The connector according to any one ofclaims 1-6 wherein said spring is a counterclockwise radial spring. 9.The connector according to any one of claims 1-6 wherein said spring isa clockwise radial spring.
 10. The connector according to any one ofclaims 1-6 wherein said spring is an axial spring having a back angle atan inside diameter of spring coils and a front angle on an outsidediameter of the spring coils.
 11. The connector according to any one ofclaims 1-6 wherein said spring is an axial spring having a back angle onan outside diameter of spring coils and a front angle on an insidediameter of the spring coils.
 12. The connector according to claim 5wherein said groove is sized and shaped for causing, in combination witha spring configuration, a force required to move the shaft in one axialdirection to be greater than 300% of a force required to move the shaftin an opposite axial direction.
 13. The connector according to claim 12wherein said groove has a tapered bottom.
 14. The connector according toclaim 13 wherein said spring is axial spring having a back angle at aninside diameter of spring coils and a front angle on an outside diameterof the spring coils.
 15. The connector according to claim 13 whereinsaid spring is an axial spring having a back angle at an outsidediameter of spring coils and a front angle on an inside diameter of thespring coils.
 16. The connector according to claim 1 wherein said groovehas a flat bottom.
 17. The connector according to claim 1 wherein saidgroove has a V-bottom.
 18. The connector according to claim 1 whereinsaid groove has a tapered V-bottom groove.
 19. The connector accordingto claim 1 wherein said groove has a semi-tapered bottom.
 20. Theconnector according to claim 1 wherein said groove has a round bottomwith a shoulder therein.
 21. The connector according to claim 1 whereinsaid groove has an inverted V-bottom.
 22. The connector according toclaim 1 wherein said groove has a V-bottom with different anglesubtending sides of said grooves.
 23. The connection according to claim1 wherein said groove is a dovetail groove.
 24. The connector accordingto claim 1 wherein said groove includes an inwardly facing lip disposedopposite a groove bottom.